Hydraulic torque converter



Feb. 20, 1940. A; Y DODGE 2,190,830

- HYDRAULIC TORQUE CONVERTER Filed Jan; 4, 1936 8 Sheets-Sheet '1 INVENTOR.

A0151. K DODa-E marnlwyfbo A TTORNEYS.

Feb. 20, 1940. A. Y. 'DODGE HYDRAULIC TORQUE CONVERTER Filed Jan; 4, 193's 8 Sheets-Sheet -2 INVENTOR. AD/EL l/Dooaz By M ATTORNEYS.

Feb. 20, 1940. A 5 2,190,830

HYDR AULI C TORQUE} CONVERTER Filed Jan. 4, 1956 a Shets-Sheet 5 INVENTOR.

ATTORNEYS.

Feb. 20, 1940. I A Y, DODGE 2,190,830

HYDRAULIC TORQUE CONVERTER Filed Jan. 4, 195a 8' Sheets-Sheet 4 IN V EN TOR.

ADIEL Y Dumas BYWZOCE k ynaufl- A TTORNEYS.

Feb. 20, 1940. A; Y. DIODGE 2,190,830

HYDRAULIC TORQUE CONVERTER Filed Jan. 4; 1936 8 Sheets-Sheet 5 f v 0 INVENTOR."

ADIELY DDDBE. 3%; J BY man/173M ATTORNEY.

Feb. 20, 1940. A. YIDODGE I'IYDBAULIC TORQUE CONVERTER Filed Jan 4, 1936 I 8 Sheets-Sheet 6 If I INVENTOR. V

AD/EL X00065 -manb +uwm A TTORNEYS.

Feb. 20, 1940. DODGE 1 2,190,830

HYDRAULIQ TORQUE CONVERTER Filed Jan. 4, 193a a Sheets-Sheet v 74', r 1; I y INVENTOR. Y AD/EL )4 D0065- ATTORNEYS.

Feb. 20, 1940. A. Y. DODGE 2,190,830

- HYDRAULIC TORQUE CONVERTER Filed Jan. 4, 1936 8 Sheets-Sheet 8 INVENTOR.

ADIEI. YT Dumas By a i ATTORNEYS.

Paemea Feb. 20, 1940 UNlTED STATES PATENT OFFICE 2,190,830 HYDRAULIC TORQUE CONVERTER Adlel Y. Dodge, South Bend, Ind. Application January 4, 1936, Serial No. 57,520

18 Claims. (Cl. so- -so' This invention relatesto hydraulic torque con-' verters and more particularly to torque convertersin which the liquid flow is toroidal.

The torqueconverter of the present invention is particularly adapted for use in a power transmission of the type illustrated in ,my 'copending applications Serial Nos. 723,083 and 34,303 and is designed to produce high operating efiiciencies throughout a wide range of torque and speed ratios. This application is a continuation in part of application Serial No. 34,303, now Patent No. 2,146,369, granted Feb. 7, 1939.

Where a torque converter is used in conjunction with a gear unit in which torque and speed ratios are changed mechanically by means of shifting gears, clutches or the like, it is desirable that the torque load on the' gears be maintained at a minimum during such shifting.- Accordingly, one of the objects of the invention is to provide a torque converter which will transmit little, if any, torque at idling speeds to facilitate shifting but which will transmit torques varying automatically from the maximum torque multito include a condition in which some such slight slip exists between the driving and the driven elements.

The above and other objects may be accom plished by providing a torque converter including an. impeller having pivoted vanes adjacent its outlet and preferably a stator having. pivoted vanes adjacent its inlet. The pivoted impeller outlet vanes assume a back angle when the turbo assembly is functioning to increase torque.

- This back angle decreases the diameter at the vane tips of the impeller, thus in effect providing a smaller impeller. In addition the back angle decreases the circumferential component, thus reducing the torque moment necessary-to turn the impeller, or permits a given torque toturnthe impeller faster. These pivoted blades are governed by centrifugal weights which tend to turn them outward toward a radial angle or' u even a slightly forward angle. The force at the blade acting against the fluid tends to tip the blade to a back angle. These forces may be balanced to get most any desired vane angle between the limits shown, and at the desired speed, and load of impeller. At 'lightloads and low speeds the vanes are nearly radial; atmedium speeds of revolution and medium torque loads the vanes become radial. At medium speeds 5 and heavy loads they are tipped to a back angle.

At'high speeds and heavy loads the vanes be come radial. If desired, the impeller may also be provided with pivoted vanes adjacent its inlet end. l

The pivoted stator vanes adjust themselves to produce a desirable entrance angle at the stator to meet the changing conditions and are preferably so arranged as to restrict fluid flow through the stator at low idling speeds? To this end 15 they maybe resiliently urgedin one direction to tend to close the flow passage through the stator and to yield as the fiow increases. at increasing speeds to permit relatively free-flow.

Another important feature of the invention 20 relates to the proportioning of .the flow areas and to the shaping thereofto'eliminate abrupt velocity changes. Preferably the impeller has a relatively large area slightly reduced at its outlet, the rotor has a smaller area decreasing from its 25 inlet to its outlet and thestator has an intermediate area decreasing from its inlet to its outlet.

- According to one arrangement, I propose to utilize a pair of connected rotors and with this 30 arrangement the second rotor preferably has an increasing area from its inlet to its outlet.' With such proportioning of the flow areas and shaping and arranging of the vanes to avoid sharp angular changes, sudden changes in velocity of 3 the fluid are eliminated. I

A further object is to provide a unit which requires no packing box around its center' shaft.

Other objects relate to a construction to eliminate or reduce friction by providing an impeller 40 casing and a skeleton rotor having open edged vanes lying adjacent to the I casing and to a novel arrangement for circulating liquid throug the converter. 1

Other advantages and novel arrangements in 45 eluding desirable elements and subcombinations will appear from the following description when 'read in connection with the accompanying draw- Figure 3a is a flow diagram of the torque converter of Figures 1 to 3';

Figure 4 is an axial section of a modified form of torque converter;

Figure 5 is an axialsection of another modifled form of torque converter; 1

Figures 6 to 10 are structural detail views of the torque converter of Figure 5;

ly on the line Iii-46, the upper half showingthe impeller vanes as they appear withthe rotor let vanes 28' are similarly pivoted adjacentithe free ends of the vanes'26. Suitable stop pins 21 carried by the impeller serve to limit pivotal .-removed, the lower left quadrant showing the rotor vanes as they appear with the stator removed and the lower right quadrant showing a section of the stator vanes on the line A-A;

Figure '16 is a diagrammatic view of a modifled impeller vane construction; and

Figure 17 is a flow diagram applicable to any of the torque converters of Figures 4, 5 or 13.

The torque converter of Figures 1 to 3 comprisesja driving shaft In which may be an engine crankshaft or an extension thereof and which is connected to an impeller casing l2. The casing is rotatably mounted in a suitable station-.-

aryhousing i4 and is sealed at its inner end against a sleeve l8 formed on or carried by the. housing. The impeller casing is formed with a series of radial passages 18 opening at their inner ends into a stationary passage 20 in the casing i4 and the casing is provided at its upper portion with a funnel member 22 and a bail'ie 24 for directing liquid into the passages l8 and 20 as will appear more fully later.

A series of inlet vanes 26 are pivoted at their lower ends on the casing l2 and a series of outmovement of the vanes26. The vane pivots carry a core member 3|) overlying the inner edges of the vanes 26' and 28 and the pivots for the vanes 28 are rotatably mounted and have centrifugal weights 32 secured thereto to control the pivotal positions of vanes 28.

A rotor-is mounted adjacent the impeller outlet and includes a sleeve 34 rotatably mounted on the driving shaft It or an extension thereof and having] a flange. 36 carrying a series of vanes 38. A core member 40 having its end registering with the core member "is secured to the inner edges of the vanes 38 and carries adjacent the inlet end of the vanes 38 a series of short vanes 42. It will be noted that the inlet ends of the vanes 38 and substantially all of the vanes 42 are. unsupported at their outer edges and lie adjacent to the inner surface of the impeller casing I2. This is an important feature since it eliminates at least aportion of the area over whichdouble casings must rotate next toeach other thereby reducingrfriction, and since the casing I2 adds a slight frictional driving efl'ect to liquid passing through the rotor vanes! Thus any friction occurring in at least this portion of the rotor vanes is not lost but is convertedinto a A statoris arranged between portion 44 mounted on the sleeve IS on a combinedv one way clutch and bearing. The one way 7 clutch and bearing may take the form of that .more fully described and claimed in my copending application Serial No. 39,674 and may include a series of anti-friction rollers 46 and a series of locking sprags 48 to permit free rotation of the stator body 44 in one direction but to prevent rotation thereof in theiopposite direction. a

The stator body 44 carries a series of fixed ating efliciency by eliminating frictional and turbulence losses and shock due to abrupt angular and velocity changes. It will be noted that the core members are irregularly shaped to provide irregular flow areas through the elements and by this arrangement and by varying the number and the thickness of the vanes the flow areas can be proportioned as desired.

The impeller is preferably formed with a substantially uniform flow area throughout the major portion of its length but is choked down at its outlet from about.2q% to 30% by decreasing the blade width to increase the velocity of discharged liquid. Considering the average area of the impeller as 100%, the areaof the rotor inlet is preferably from 30% to 50% and the rotor area decreases toward the outlet to from 20% to 30%. The stator inlet is preferably somewhat larger than the rotor outlet and the stator likewise decreases in area toward its outlet to substantially the sarne size as the rotor outlet. While it might ordinarily be undesirable to discharge liquid from the stator outlet into the impeller inlet at high velocity, particularly at such times as when the stator is rotating for-. wardly, the objections and undesirable features are largely overcome by the pivoted impeller this flgure theimpeller is marked 1, the rotor-R and the stator S. As shown, the impeller inlet has an area of about 73 square units with a maximumimpeller area of 100 and an outletarea of 50. The rotor-inlet has an area of 50 tapering to 30 at the outlet, and the stator inletis shown with-an area of 42 tapering to 30 at the outlet. with thearrangement above described, the flow velocity through the impeller 'is low and the velocity through the rotor and st'ator is relatively high. Thus a high pressure is built up in the impeller which imparts energy to the rotor both through the conversion of the pressure into velocity and through the change of direction of the fluid, the stator again changing the direction of the fluid and providing afulcrumfor torque multiplication. The small vanes" 42 at the rotor-inlet serve both to restrict the flow area and .to reduce turbulence by dividing the liquid into smaller streams. v

Thevanes are also .so shaped as to provide a smooth flow contour as best seen in Figure 2. It will be noted that the pivoted vanes 54 are arranged so that their outlet ends will lie closely adjacent the inlet ends of the vanes 50 so that 7 fluid can pass from one set of vanes to theiother substantially without shock. The vanes 28 are preferably similarly located with respect to the,

vanes 28. Also if desired, the pivoted vanes may be pivoted intermediate their ends as indicated in case of the vanes 84 in Figure 2 to produce a partially balanced vane requiring less effort to i turn it against the fluid reaction. When the impeller is turning slowly ,the weights 32 exert very little force on the vanes 28 and fluid reaction turns them to the dotted line position of Figure 2. Liquid will therefore leave these vanes with a high radial and a low circumferential component and will pass through the rotor vanes 38 and 42. The'stator vanes 54 will be held in their fullline position by the springs 58 and will partially block the flaw offluid through the stator. The fluid will leavethe stator with a forward circumferential component and strikethe backs of the vanes 26, urging theminto their dotted line position.

Under these conditions, which obtain during idling or very'slow impeller speeds, very little force is transmitted to the rotor and change speed gears or clutches can be shifted readily or a vehicle or machine will stand with. very little tendency to creep. i

It is apparent and'well known that the quantity flow of fluid is much higher through such a system when the rotor is standing or moving slowly, and the impeller is turning fast, than is the case later when the rotor turns at the same speed as the impeller.. This is due to the lack of counter centrifugal head when the rotor is standing As the impeller speed increases the weights 82 tend to move the vanes 28 toward their full line position, but can not do so due to the large quantity fluid flow. The liquid leaving the impeller strikes the rotor vanes with a high forward component and is reversedthereby toimpart a forward driving force to the rotor, the liquid leavferential component and will strike the stator' vanes ontheir backs, thereby turning the stator forwardly. -At this time the stator is ineffective and the converter operates substantially as atwo element clutch.

Liquid will be circulated through the torque converter during operation in order to maintain the converter full of liquid and to cool the liquid. For this purpose the casing i4 is preferably partially filled with liquid and as the converter rotates, it causes the liquid to swirl in the casing.

The baiiie 24 turns a portion of the swirling liquid into the funnel 22 which directs it into the passage 28 and the inner end of the radial passages I8. Centrifugal force causes the liquid to flow outwardly in the passages I8 and into the torque converter through the space between the stator and the impeller.

-As pressure builds up in the torque converter the liquid will be'forced out between the impeller, the rotor and the stator and'will lubricate the several bearings. Suitable packlngs are preferably provided to prevent escape of liquid along ,which is rotatable on shaft i8.

theshaft'lfl or sleeve 84 and a spring loaded insure an ample supply of liquid, the casing i4 115 preferably provided withtanks 68 (Figure 3) communicating with the housing i4 through a tangential inlet 8i at the bottom and a top vent 82. During rotation of the impeller casing liquid will be forced into the tanks through the tangential inlet 6i until only a relatively small amount of liquid remains in the housing i4.

However, should the amount of liquid in the housing decrease, the pressure on the-inlet 6i would decrease, causing liquid to back up from the tanks 80 to maintain a supply of liquid in the housing without requiring the torque converter to rotate in a large body of liquid.

Since the liquid in the torque converter is liable to become so hot as to cause vaporization under some conditions, there is preferably provided a condenser to condense any vaporized liquid and return it to the converter. As shown in Figure 3, a condenser 63 which may take the form of a conventional automobile radiator is connected by a pipe 84 with the housing l4. Any vapor generated in the housing during operation will rise through the pipe 64 into the condenser 83 where it will be condensed and returned to the housing through a pipe 65 having a tangential inlet into the housing. Preferably the condenser is provided with a vent 861:0 prevent building up high pressures therein. g

Figure 4 illustrates another form of hydraulic torque converter in which the shaft ill is connected to and drives an impeller casing 10 which formsan outer liquid-tight housing for the entire unit. A series of rigid vanes 12 are secured to the impeller casing and a second series of vanes 14 are secured adjacent the upper or outlet ends of the vanes 12 on pivots 16 which are journaled in the impeller casing 18 and an annular ring 18 which is. fastened to the inner edges of the vanes 12. Thering 18 has a feed opening 80 therein for the purpose of feeding liquid into the impeller vanes. The pivoted vanes 14 are controlled automatically by centrifugal weights 82 secured to theaxles 1.8 and arranged to tilt the vanes forwardly under the influence of centrifugal force. Preferably the. weights 82 are so arranged that their centers of gravity will lie substantially on a radius through the axles 16 when the vanes 14 are tilted rearwardly to reduce the c1" centrifugal force at low rotor speeds as more fully set forth in my copending application Serial No.

3,544 filed January 26, 1935. Stop pins 84 (Figure 11) are preferably provided to limit the pivotal movements of vanes 14.

.A double driven rotor is arranged adjacent, the impeller vanes and is carried by the sleeve 28 As shown the rotoris constituted by a set of fixed vanes 86 mounted adjacent the impeller vanes 14 and a unit and to vent air from the unit as will appear hereinafter.

Between the outlet of rotor vanes 88 and the inlet of rotor vanes 99 a stator ls'mounted, constituted by a sleeve 94 rotatable on the sleeve. 20 and carrying a series of fixed vanes 90 and a series of vanes 99 mounted on hollow pivots I which are journalled in an annular plate or flangeon the sleeve 94 and a ring I02 which is fastened to the inner edges of the vanes 99. A spiral spring I04 is connected to each of the pivots I00 and tends to'tllt the vane 99 forwardly with respect to the direction of rotation of the impeller. Each of the pivots I00 carries at its inner end a lever I06 (Figure and the levers have pins at their free ends which project through radial slots in a ring I08 to insure that all of the vanes 99 will move together.

In order to obtain high emciences with a hydraulic torque converter,,I have found that it is extremely important to correctly proportion the areas of the flow passages through the impeller, the rotors and the stator to vary the velocity of flow through these elements. I have discovered that the best results can be obtained with a relatively low flow velocity through the impeller, a high flow velocity increasing from the inlet to the outlet through the first rotor, a high flow velocity through the stator, and a flow velocity decreasing from the inlet to the outlet in, the second rotor to convert as much flow velocity into static pressure as is consistent with efliciency. I have also found that where liquid at high velocity is subjected to a rather abrupt velocity change by a set of vanes, turbulence is apt to result, thus decreasing the efliciency. of the hydraulic unit.

According to the present invention and as best seen in Figure 12, these desirable results are attained and turbulence is prevented by designing the impeller with flow passages of larger area than the other elements and proportioning the areas through the other elements to obtain the desired flow relationships, 'it being understood that this proportioning is followed in all. of the illustrated embodinients. The relationships will vary with varying conditions and requirements but in general thevelocity through the first rotor should be from one and one-half to two and onehalf times that through the impeller. The rotor vanes are preferably thickened adjacent their inlet ends to decrease the flow area at this point and auxiliary vanes 81 are mounted between adjacent rotor vanes at the inlet ends thereof and extending through from one third to one half of the length of the rotor vanes. The auxiliary vanes 91 serve both to restrict the flow area further in the rotors and to. divide the incoming liquid into a plurality of small streams, thus reducing turbulence. It will be noted. that the sharp curve of the main rotor vanes causes the flow area to decrease toward the outlet end, this eflect being'augmented inthe case of the outer rotor bythe decreasing radius of the discharge ends of the vanes.

In the arrangement of Figure 4, the converter is enclosed in a casing I I0 havingventilation openings therein and which is connectedv to a gear casing H2. The gear casing is preferably, adapted to contain oil or other suitable liquid for use in the hydraulic unit and such liquid is given a swirling motion in the gear casing by rotation of the gears therein orby some other suitable element driven by the driving shaft. Adjacent the top of the gear casing a baille I I4 is secured to divert the swirling oil into a feed cup H9 which communicateswith a centrifugal pump III carrledby the impeller casing II. The pump Ill is preferably constituted by a.

plurality of radial passages communicating with torque,

the hollow pivots I00 so that liquid from the cup H9 will be forced through the pump H0 and pivots I00 into the center or core of the vane structure and'out through feed ports 80 into the vanes.

As pressure builds up in the vanes, liquid will flow out between them through passages I20 and I22 and through the bores 92 and around the shaft. bearings back to the gear casing. Thus a constant circulation of liquid is maintained when the unit is in operation to prevent the liquid from becoming overheated and at the same time to provide lubrication for the parts.

Preferably the liquid level in the gear casing is below the shaft bearings to reduce the tendency for leakage while standing and to eliminate.

through an automatic clutch to turn forwardly at reduced speed at high rotor speed. As shown,

.the stator is held against reverse rotation by a combined bearing and one-way clutch I26 which acts between the sleeve 94 and a stationary part of the casing and the sleeve 94 carries a set of forward component due to high rotor speed, the stator will be rotated forwardly to pick up the liquid and discharge itinto the second 'rotorwith' a forward component. This reduces shock in the liquid which might occur if it entered the second set of, rotor vanes in aradial directionand contributes'to smoother operation and increased eiilciency at high speeds. Also since the liquid may leave the second rotor vanes with a for-j ward component, indicating that all of the energy has not been extracted therefrom, the rotor, under proper conditio'ns'will be driven faster than the impeller and at lower torque.

Figure 5 illustrates a modified hydraulic torque converter, parts therein which are the same as parts in Figure 4 being indicated by the same reference numerals. In the modification of Figthis arrangement when the liquid leaves the first rotor substantially radially or even with a slight ure 5 the hydraulic-unit is enclosed in a housing I I I which is adapted to contain liquid and liquid is circulated from this housing through the hydraulic unit. As the hydraulic unit rotates it causes a swirl of liquid in the housingl II which is deflected by a home II! into a feed cup II! from which it flows into the pump III and through pivot I into the vanes as in the con struction of Figure 4. "However, instead of the liquid flowing back-along the shaft I2 it passes from passag I22 past a check valve I2I directly back into the casing III. Any liquid passing through passage I20 will return directly to the inlet of the pump III and any liquid leaking.

past the bearings along the shaft II isdrained through the casing III back to the pump inlet through ports I25, leakage being prevented by oil slingers I21 on the shaft I2 and sleeve 20. p

Figure 5 also serves to illustrate a manual control for the pivoted stator vanes by which the automatic control can be over-ruled and, ii'de-' engages one end of a crank I38 which is jour-.-

nailed in the sleeve 94. The other end of the crank I38 is formed as a worm and engages a worm gear formed on or secured to the pivot I00 so that rotation of the crank I38, turns the pivot I00 to adjust the stator vanes 98.

The collar I36 is moved by a crank I40 which is journalled in the casing III and one end of which engages the other groove in the collar I36, Thus rotation of the crank I40 slides collar I36, turns crank I38 and adjusts the vanes 98. The other end of the crank I40 projects and terminates in a notched button I42 which is rigidly'secured thereto. A lever I44 is freely mounted on the crank I40 and carries a spring pressed detent I46 which is adapted to engage the notch in button I 42 to secure the lever to the, crank. The detent I48 preferably has a rod extending through the lever I44 and terminating in a button I48 having 2. lug

thereon adapted to fit into a notch in the end of the lever to permit the detent to move into operative position or to engage the end of the lever to hold the'detent out of operation. In the last named position the cranks are freeto turn to permit automatic adjustment'of the vanes 98 without moving the lever. I44.

In order to lock the lever and, if desired, the vanes 38 in any desired position, a segment I50 is mounted on the casing III and the lever I44' carries a pawl I52 engageable with the segment. When the pawl is in engagement with the segment the lever I44 cannot be moved but when the pawl is free of the segment the lever can be moved at will. Preferably the pawl is pressed into engagement with the segment by a spring and a handle I 54 is provided to move th pawl.

As best seen in Figure 11 the casing III- oi. Figure 5 is formed with a tank I 63 communicating with the casing through a tangential inlet I51 and a vent I88. During operation liquid will be forced into the tank I66 through the tangential inlet to lower the level of liquid in which the torque converter rotates in the same manner as prevlouslydescribed in connection with Figures 1 to 3. The casing III may also, if desired, be provided with inlet and outlet connections I8I and I83 respectively for connection with a condenser such as 03 in Figure 3.

Figures 13 to 15 illustrate a further modifiedarrangement of a torque converter having a, double rotor and for the sake of brevity of deinto alinement with either of two adjacent stator vanes 36 to provide smooth flow passages as best seen in Figure 14.

Liquid is supplied to the converter from any convenient source such as an engine driven.

pump through a pipe H9 which communicates with the-centrifugal passage II 8. From here liquid is forced into the torque converter through the hollow pivots I00 in the manner previously described. Liquid is circulated out of the torque converter between the several elements into" a passage II formed in the drive shaft I0, a suitable spring loaded valve I3 being provided to control the outlet of liquid. Liquid passing the valve I3 may be cooled, if desired, and returned to the source to be again circulated throughthe pipe I I9. This arrangement insures that the torque converter will be maintained full of liquid, the valve I3 being set to maintain any desired pressure therein.

It will be noted, particularly from Figure 15, that the weights 82 extendin the general direction 01 the pivoted vanes". At the left of Figure 15 the vanes and weights are shown in the position they will occupy at low speeds and atthe right in the position they will occupy at high speeds. This positioning of the weights produces a different centrifugal force characteristic than the position shown in the preceding figures but the operation of the pivoted vanes I4 is, in general, substantially the same as that of the preceding figures.

The flow areas of the torque converter of Figures 13 to 15 are generally the same as in the previously described embodiments with a large area, low veloclty'impeller, a high velocity first rotor and stator and a relatively low velocity secondrotor. Where a low velocity second rotor is employed it is generally not necessary to pivot the stator inlet vanes to avoid the undesirable features arising from a high velocity dischargeinto the impeller inlet. However under some circumstances it maybe desirable and in this event an impeller may be arranged as indicated in Figure 16 having pivoted inlet vanes I2 and pivoted outlet vanes 14'-controlled by weights 82'. Suitable stops I3 are preferably arranged to limit the movement of the vanes 12' so -that the free ends of the vanes 12' will lie adjacent the pivoted ends ofone or another of the vanes I4" to provide smooth flow passages.

Figure 1'7 is a flow diagram of a four element torque converter illustrating the relative flow areas and applies equally well to any of the torque converters of Figures 4, 5 or 13. In this figure the impeller is designated- I, the first set of rotor vanes R1, the stator S and the second set of rotor vanes R2. The areas through theim peller, first rotor vanes and stator are substantially the same as indicated in Figure 3a and the second set of rotor vanes have an area oi about 43 square units at their inlet and 83 at their outlet. I

While several embodiments of the invention have been illustrated and described in detail, it will be apparent that many changes might be made therein and it is not intended to be limited to the forms shown nor otherwise than bythe terms of the appended claims.

"What is claimed is l. A hydraulic torque converter comprising an impeller, a stator and a rotor, the impeller including a plurality of vanes including outlet portions pivoted on elongated shafts, and having centrifugal weights mounted on said shafts and impeller inlet and a plurality'of vanes pivoted.

6 directly connected to the vanes to control the position of said vanes about their pivots and the stator including vanes pivoted adjacent their inlet ends.

2. A hydraulic torque converter comprising an impeller, a stator, and a rotor, the impeller including a plurality'ofv fixed vanes adjacent the adjacent theimpeller outlet on elongated shafts journaled in the impeller, centrifugal weights mounted on said shafts and connected to said pivoted vanes to control their positions, and the stator including a plurality of vanes having pivoted portions adjacent their inlet ends and. fixed portions adjacent their outlet ends. n

3. A hydraulic torque converter comprising an impeller, a rotor having two sets of vanes a cent the ends of said impeller, a reaction mem er between said sets of rotor vanes and a gear chain having a plurality of elements, one of which is fixed and two others of which are connected to i said rotor and said reaction member respectively so that the reaction member may impart forward torque to the rotor or the rotor may impart forward torque to the reaction member depending upon the direction of impingement of the liquid against the reaction member.

4. A hydraulic torque converter comprising a hydraulic unit, a casinginclosing said unit, means for circulating liquid from the casing through said unit and back tothe casing, and a conclens'er connected to the casing for receiving vaporized liquid therefrom and for returning condensate thereto.

5. A hydraulic torque converter comprising a vaned impeller, a vaned rotor and a vaned stator forming a fluid passage,,said vaned impeller including fixed vanes at its inlet end and pivoted vanes adjacent the impeller outlet pivoted on elongated shafts and centrifugal weights connected to said shafts for urging said pivoted vanes in one direction, fluid reaction. tending to urge the vanes in the opposite direction.

6. A hydraulic. torque converter comprising a varied impeller, 'a vaned rotor and a vaned stator forming a fiuid passage, said impeller including a A set of pivoted vanes adjacent its outlet end and a set of pivoted vanes adjacentits inlet end, the

, free ends 01' said last set of vanes lying adjacent and a vaned stator member forming a liquid cirthe pivots for said first setof vanes.

7. A hydraulic torque converter comprising a vaned impeller, a vaned rotor and a vaned stator forming a fluid passage, said impeller including a set of pivoted vanes adjacent its out-.- let end and a set ofpivoted vanes adjacent its inlet end, the free ends of said last set of vanes lying adjacent the pivots for said first set of varies, and said stator including a set of pivoted, vanes adjacent its inlet end.

8. A hydraulic 'torque converter comprising a vaned-impeller having a series-of pivoted vanes adjacent its outlet end, a vaned stator having a series of pivoted vanesv adjacent its inlet end, and a rotor having two sets of vanes lying between I said impeller and said stator.

9. A hydraulic torque converter comprisin avaned impeller member, a vaned rotor member cult, one" of said members having a series of pivoted vanes, hollow pivots on which said pivoted vanes are mounted, and means to supply liquid to said-hollow pivots whereby said liquid may flow through the pivots into the torque converter.

1 -:,10. A hydraulic torque converter comprising a vanea .inpeller, a vaned rotor and a vaned sta tor forming a liquid circuit, said stator having a series of pivoted vanes adjacent its inlet end, hollow pivots on which said pivoted vanes are mounted, and means to supply liquid to said hollow pivots whereby said liquid may flow through.

series of pivoted vanes adjacent its inletend,

.hollow pivots on which said pivoted vanes are mounted, and means forming substantially radial passages in the impeller communicating with said pivots to supply liquid to said pivots and therethrough to the torque'converter.

12. A hydraulic torque converter comprisinga vaned impeller, a vaned rotor and a vaned stator, said impeller having a series of fixed inlet vanes and a series of outlet vanes pivoted adjacent their inlet ends and tiltable from a position in which they form aback angle with radii passing through the pivot points into a position in which they form a forward angle with the radius.

13. A hydraulic torque converter comprising a vaned impeller, a vaned rotor and a vaned stator, said impeller having a series of fixed inlet vanes and a series of outlet vanes pivoted adjacent their inlet ends and tiltable in response to liquid pressure thereon to a position in which they form a back angle with radii passing through the pivot points and centrifugal means for tilting said vanes into a position in which they form a forward angle with the radius.

14. In a hydraulic power transmitting device comprisingdriving and driven elements, and a reaction element, each of said elements being provided with a series of fixed vanes which form radial passages through which the liquid flows from one element to the other in a closed circuit, the

provision in the driving element, between the inlet end of the radial passagesthereof and the outlet end of the radial passages of the preceding element, of an annular space within which are positioned a series of freely pivoting 'vanes each of which is separately mounted in the side walls of the driving element so as to lie in the path of the liquid and is acted upon by said liquid independently of the others, sothat when a change of speed occurs between the driving and driven elements, the said pivotal. vanes are automatically adjusted by a changing angle of impingement into such a position as will afford the most appropriate guidancefor the passage of liquid from one element to the other.

15. A hydraulicpower transmitting device as claimed in, claim 14 in which an annular space is also provided in the reaction element, between the inlet end of the radial passages thereof and the outlet end of the radial passages of thedrlven element, a series'of freely pivoting vanes being positioned within the said space, each vane being separately mounted inthe side walls of the reently of the others, so that when a change of speed occurs between the driving and driven elements, the said pivotal vanes are automatically adjusted by a changing angle of impingement into such a position as will afford the most appropriate guidance for the passage of the liquid from one element to the other. n

16. A hydraulic power transmitting apparatus as claimed in claim 14 in wl'iich the reaction member is provided with a one-way clutch and is thereby capable of free movement in one direction, but remains stationary when a force is applied in the opposite direction.

1'7. A hydraulic power transmitting apparatus as claimed in claim 14 in which as the angle of impingement of the liquid'in leaving one rotating part changes, due to alterations in the load conditions, so the, liquid acts upon one side or the other of the series of pivoted vanes to automatically position them so that they afford to the moving liquid the most appropriate guidance to minimize disturbance in the liquid flow.

18. A hydraulic power transmitting apparatus as claimed in claim 14 in which the vanes are of 5 aeroioil section.

ADIEL Y. 

